Transmission controls



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TRANSMISSION CONTROLS 8 Sheets-Sheet 6 Filed June 2l, 1954 juz/e xfoa ZU foldsmm and Aug. 30, 1960 .1. w. HOLDEMAN E T AL TRANSMISSION CONTROLS Filed June 21, 1954 8 Sheets-Sheet 7 m E m @o H. M n ,m J

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TRANSMISSION CONTROLS 8 Sheets-Sheet 8 Filed June 2l, 1954 www htates 2,950,629 Patented Aug. 30, 1960 TRANSD/HSSHON CNTRGLS .lohn W. Holdeman and John B. Polomski, Detroit, Mich., assignors to Borg-Warner Corporation, Chicago, lll., a corporation of lilinois Filed June 21, 1954, Ser. No. 438,079

16 Claims. (Cl. 74-472) Gur invention relates to transmissions and more particularly to transmissions for heavy vehicles such as trucks.

it is an object of the present invention to provide improved hydraulic controls for a transmission having five different speed ratios in forward drive, and it is an obiect to provide selecting means under the control of the vehicle operator whereby he may at his option select either first, second or third speed ratios for completion in the transmission or he may select an automatic range in which the initial drive is through the second speed ratio and automatic changes to third and fourth speed ratios subsequently take place as the speed of the vehicle increases or he may select still another automatic range in which the same automatic ratio changes take place except that a nal automatic change is made into the fth speed ratio.

it is also an object of the invention to provide improved mechanism for preventing excessive speeds of the vehicle engine and particularly for preventing a change from a higher to a lower speed ratio when the speed of the vehicle is so high that excessive engine speeds would result.

it is contemplated that the second speed ratio may be completed by either a friction engaging device or a oneway engaging device, and it is an object of the invention to so arrange the controls that when the second speed ratio is obtained at the option of the driver, exclusive of either of the automatic ranges, the friction device is utilized for completing the power train so that this is a twoway power train, while the one-way device is utilized for completing the power train in either of the automatic ranges.

. it is another object of the invention to provide a plurality of shift valves, each of which causes a change in speed ratio through the transmission, and each of which is responsive to two governor pressures that are applied in accordance with changes in speed of the vehicle and the transmission driven shaft. It is contemplated that one of the governor pressures shall be eifective for allowing an upshifting movement of the valve and that the other governor pressure is effective for holding the valve in an upshifted position once it is in this position, as long as the vehicle speed remains above a certain value. it is also an object of the invention to provide nid how restricting mechanism in connection with servomotors for transmission brakes and clutches, so that the brakes and clutches may be engaged to give smooth changes in drive under various vehicle operating conditions, and it is an object to provide one of the clutches with a Belleville type washer between the clutch enpiston and the clutch plates which provides smooth changes of ratio with a minimum of valving.

The invention consists of the novel constructions, arrangements and devices to be hereinafter described and claimed for carrying out the above-stated objects and such other objects as will appear from the following 2 description of preferred embodiments of the invention, illustrated with reference to the accompanying drawings, wherein:

Fig. l is a schematic diagram of a transmission with which our improved controls may be utilized;

Fig. 2 is a table showing the various clutches and brakes which may be engaged to complete Various power trains through the transmission',

Fig. 3 is a diagram showing how Figs. 4, 5, 6, 7, 8 and 9 should be laid together in order to form a complete showing of the controls for the transmission illustrated in Fig. l;

Figs. 4, 5, 6, 7, 8 and 9 are parts of the transmission control system of the invention which should be laid together in the manner shown in Fig. 3;

Fig. 8A is a portion of a modilication of the transmission controls which can be substituted for Fig. 8 for showing the modification of the controls;

Fig. l0 is a longitudinal sectional View of a clutch forming a part of the modified controls; and

Fig. 1l is a graph showing the engaging characteristics of the clutch illustrated in Fig. l0.

Lilie characters of reference designate like parts in the several views.

Referring now to Fig. l showing the transmission with which our improved controls are adapted to be utilized, the transmission comprises a drive shaft 2t?, a driven shaft 2l, a pair of intermediate shafts Z2 and 23 coaxially disposed with respect to the shafts 2@ and 2l, and sleeve shafts 24 and 25 respectively disposed over the shafts 22 and 23. The drive shaft 20 is adapted to be riven from the engine (not shown) of the vehicle in which the transmission is installed, and the driven shaft 2l is adapted to drive the road wheels (not shown) of the vehicle.

The transmission comprises, in general, a iluid coupling 26, planetary gear sets 27 and 28, a one-way brake 29, friction band brakes 3h, 3i and 32, and friction disk type clutches 33 and 34.

The planetary gear set 27 comprises a sun gear 3S, an elongated planet gear 36, a ring gear 37, a planet gear 38, a sun gear 39, and a carrier 40 for the planet gears 3S and 36. Fthe planet gear 36 is in mesh with the sun gear 35 and with the ring gear 37, and the planet gear 33 is in mesh both with the planet gear 36 and with the sun gear 39. The sun gear 35 is connected with the shaft 22, and the carrier itl is connected with the shaft 23.

The planetary gear set 28 is of the same type as the gear set Z7 and comprises a sun gear 4l, an elongated planet gear 42, a ring gear 3, a planet gear 44, a sun gear 45 and a carrier 46 for the planet gears 42 and 44. The planet gear 42 is in mesh with the sun gear il and with the ring gear 43, and the planet gear 4.4iis in mesh both with the sun gear 45' and with the planet gear 42. The sun gear 4l is connected with the shaft 23, and the carrier 46 is connected to the driven shaft 21 of the transmission.

The friction brake 39 comprises a friction drum 47 connected with the ring gear 37 and a friction band 4S adapted to be contracted to engage the drum 47. Tue drum 47 is connected to the one-way brake 29 which may be of any suitable construction and is shown to comprise a plurality of tiltable grippers 49 acting between an inner race 5i) connected with the drum 47 and an outer race 51 connected with the casing 52 of the transmission and held stationary thereby. The one-way brake 29 functions so as to allow the drum 47 to rotate in the forward direction, that is, in the same direction as the drive shaft 2i) of the transmission is driven from the vehicle engine,

but prevents rotation of the drum 47 in the opposite directionf Ihe clutch 33 comprises a` plurality of clutch disks 53 (see Eigfl) `connectedwith theshaft 24, a plurality of clutch Vdisks 54connected with the drum 47 and armovf able piston 55 for pressing the plates 53 andV 'ligintoV frictionalinterengagement A. Y Y Y Y, y The brake 31 comprises a brake drum 56 connected with the sun Ygear 45 and Vengageable by a gbrake band 57. The clutch 34 comprises a plurality of friction plates 58 (see Fig. 7), a plurality of friction plates 59 and a K piston 60.` The plates 58 are connected with the drum 56, andthe plates 59 are connected with the shaft 25. The pistonY 60Y is adapted to move the plates 58 and 59 into frictionalinterengagement. 'The brake 32 comprises a drurnV 61 .adapted tober engaged by a brake band 62.

' The ringggear 43'is fixed in the drum 61.

The fluid coupling 26 comprises an impeller 63 provided witha pluralityY of vanes 64 and connected to the shaft 20Y anda turbine or a driven element 65 also provided with a plurality of vanes 66 arranged opposite the variesY 6,4and connected with the-shaft 22. The fluid coupling 26 is of conventional construction and'hence need not be described in detail. The vanes 64 and 66 are disposed in the same uid container, so that, when the impeller 63 is rotated; the, vanes 64 of the impeller set up a toroidal fluid motion and transmit torque through the uid to the turbine Yelement 65. The shaft 24 is connected with the impeller 63 and is thus driven directly from the shaft Y20. The planet gear carrier 40 is provided with a ring gear 67, and a gear 68 is adapted to be shifted into mesh with the gear 67, so that the gear 68 may be driven for power take-off purposes.

A neutral condition of the transmisison is obtained when all of the brakes 30, 31 and 32 and the clutches 33 and 34 are disengaged (see Fig. 2). A neutral is also obtained if the brake 30 is engaged, with the remaining brakes and clutches just mentioned remaining disengaged. The brake -30 is actually in parallel with the one-way brake 29, which incidentally is always effective on the ring gear 37. With the one-way brake 29 being effective either with or Vwithout engagement of the friction brake 30, the carrier 40 is driven through the fluid coupling 26; however, since Vall. of the brakes and clutches for the second planetary gearing 28 are disengaged, no power is transmittedV to the driven shaft 21. Inasmuch as the carrier 4.0 is driven from the drive shaft 20, however, the ring gear 67 in conjunction with the shiftable gear 68 may be used for power take-off purposes. The one-way brake 29 functions to hold the ring gear 37 against reverse rotation, Land the sun Agear 35 is driven from the drive shaft 20, through the impeller 63, the runner 65, and the shaft 22. The sun gear 35 when thusY driven causes rotation of the carrier 40 in the forward direction i .M Y:2,950,629

at a reduced speed with respect to that of the drive shaft 20L The friction brake 30 which is in parallel with the one-way brake 29 assures that the drive of the lcarrier 40 and ring gear 67 is a two-way drive instead ofv a oneway drive, in view of the fact that the one-way brake 29 may overrun.

Low or first speed forward drive'may be obtained through the transmission by engaging the brake 32. The one-way brake 29 may be utilized for providing a drive through the first planetary gear set 27, and the brake 30 mal also be engaged, augmenting the action of the oneway brake 29, if desired. VThe planet gear carrier 40 is driven through the first planetary 27 and fluid coupling 26 as described above in connection with neutral condition of the transmission, and the carrier 40 drives the shaft 23 and the sun gear 41 of the second planetary gear set 28. The brake 32 functioning on the drum 61 causes the ring gear 43 to function as the reaction element of the second planetary gear set 28, and the Vdrive Y 4 proceeds through the planetary gearing 28 to the carrier 46 of the gear set 28 and the driven shaft 21.

Second speed forward drive through the transmission is obtained by disengaging the brake 32 and Aengaging the brake 31, either utilizing the one-way brake 29 for the first planetary gear set 27 alone Or in conjunction with the brake 30. Tli'e'"planef` gear carrier 46 of the first planetary gearset 271is driven as before and rotates the sun gear 41 of the second planetary gear set 28. The brake 31 in this case causes the sun-gear 45 to funetion as the Vreaction element of the Vplanetary gear set 28, so that the carrier `46 in this case is driven at a higher speed than in low speed drive but at a reduction in speed with respect to that of the shaft 23. The driven shaft 21 rotates along with thecarrier 46V at this'increased speed.

Third speed forward drive is obtained by keeping the brake 31 engaged and engaging the clutch 34, allowing the 'brake 30 to disengage. The clutch 34 in this case functions actually as a brake,V and the band 57 of the brake 31 is effective to brake the sun gear 45 of the second planetarygear set 28 as in second speed forward drive, and, through the clutch 34, the band 57 lalso brakes the sun gear 39 of the first planetary gear set 27. The two sun gears 45 and 39 now function as reaction elements in the planetary gear sets'27 andZS, respectively. The drive in this c ase is from the drive shaft 20 through the fluid couphng 26, the shaft 22, the sun gear 35, the planet gears 36 .and 38, the carrier 40, the Vshaft 23, the sun gear 41, the planet gears 42and 44 and the planet gear carrier 46 to the driven shaft 21. Since, for third speed drive, the sun gear 39 is held stationary instead of the ring gear 37, the shaft 23 in this case is driven at a higher speed than for the second speed forward drive, and in this case the one-way brake 29 overruns.

For fourth speed forward drive, the clutch 33 is engaged; the brake 31 remains engaged; and the clutch 34 is disengaged. 'Ihe drive through the first planetary gear set 27 in this case is in two paths. IOne path is through the fluid coupling 26 and the shaft 212 to the sun gear 35, while the other path is through the impeller 26 to the shaft 24 and the clutch 33 to the ring gear 37. When there is substantial speed of the drive shaft Ztl, the sun gear 35 rotates substantially at the speed of the drive shaft 20, as there is little slip in the fiuid coupling 26, and the clutch 33 connects lthe ring gear 37 directly with the drive shaft 20, so that the parts of the planetary gear set 27 all rotate substantially at a one to one ratio and drive the shaft 23-connected with the carrier 4? substantially at the speed of the drive shaft 20. The drive in fourth speed ratio through the planetary gear set 28 is the same as that in third speed ratio, since the same sun gear 45 is held stationary as the reaction element of the gear set 28.

For fifth speed forward drive, the brake 31 is disengaged and the clutch 34 is engaged, with theclutch 33 remaining engaged. 'Ihe drive in this case through the first planetary gear set 27 is the same as in fourth speed forward drive, with all of the parts of the gear set Z7 rotating at substantially the same speed as the drive shaft 20. In theV case of fifth speed forward drive, however, two pathsrof power flow proceed from the first planetary gear set 27., one path being from the planet gear carrier 40 through the shaft 23 to the sun gear 41, and the other path being from the sun gear 39 through the sleeve shaft 25 and the clutch 34 to the sun gear 45. The drive proceeds through the planetary gears 44 and 42 ofthe planetary gear set 28 to the carrier 46 and the driven shaft 21, with the parts of the second planetary gear set 28- substantially all rotating at the same speed.

Reverse drive is obtained by engaging the clutch 34and the brake 30. The brake 30 is effective on the ring gear 37, and the sun gear 35 is driven as before from the drive shaft 20 through the fluid coupling 26. The carrier 49 of the gear set 27 is driven at a reduced speed in the forward direction, as in certain previous drives, and drives the sun gear 41'through-the shaft 2:3. The suny gear 39v of the first planetary gear set 27 under these conditions is driven at a faster speed than the carrier 49 but in the reverse direction, and this rotation is transmitted to the sun gear 45 of the second planetary gear set through the clutch 34. The resultant of the rotations of the sun gear 45 and the sun gear 41 is a rotation in the reverse direction of the planet gear carrier d6 of the second planetary gear set and a corresponding rotation of the driven shaft 21.

Since the brake 3!) is the only reaction member in the transmission for reverse drive, the ring gear 37 tends to spin forwardly, and the freewheel unit 29 is not effective in restraining forward rotation. The brake 3i? thus takes the complete reaction for the reverse drive. The brake 3U, incidentally, is so arranged with respect to its apply piston eifective on one end of the brake band 43 and a i'ixed reaction point on the other end of the band that the brake wraps or is self-energized for the reverse drive through the transmission and tends to unwrap or is deenergized for the forward drives for which the brake 30 is eiective. This is so because the ring gear 37 tends to rotate in a counter-clockwise direction with regard to the brake 3@ in its position shown in Figure 4 for reverse drive and in a clockwise direction with regard to the brake 39 in its position shown in Figure 4 for the forward speed drives for which the brake is effective.

lt will be observed from a consideration of the various drives just mentioned that the carrier 4@ is driven in the forward direction for all of the various drives, and thus the power take-oftgear 68 may be utilized for all the drives, when in mesh with the gear 67, for power take-ofi purposes.

A person skilled in transmission design can be expected to be able to design a working transmission from the schematic showing of Fig. l as described above; however, for any details of design, if any are desired, the copending application of l ames A. Miller, Serial No. 429,268, tiled `May 12, 1954, may be referred to, this patent application showing the same transmission as has just been described. The ratios listed in Fig. 2, incidentally, are obtained from an actual embodiment of the transmission with gears of a certain size, and the gear sizes and ratios may be changed if desired, asis apparent.

rihe controls for the transmission comprise, in general, a front oil pump 75 driven from the drive shaft 25 of the transmission, a rear oil pump 75 driven from the driven shaft Z1 of the transmission, a selector valve 77, a governor valve 78, a downshift inhibitor valve 79, a push start valve 80, a modulator valve `31, a pressure regulator valve S2, a coupling valve 83, a reverse interlock valve 84, a free wheel valve S5, a second speed valve 86, a third speed valve 87, a fourth speed valve 83, a ifth speed valve 89, a 5-4 shift valve 9i?, and a lubrication valve 91.

vThe pump 75 comprises a pump casing 92 having an oblong cavity 93 therein. A casing 9e, also oblong in shape, is slidably disposed in the cavity 93. The casing 9d has a cylindrical cavity 95 therein, and a cylindrical rotor 95 is rotatably disposed in the cavity 95. The rotor 96 carries a plurality of vanes 97 slidably disposed in slots in the periphery of the rotor which Contact the surface of the cylindrical cavity 95 on the ends of the vanes. The rotor 96 is driven from the drive shaft 2@ of the transmission by any suitable means. A compression spring 93 is disposed between the lower end of the casing 94 and the bottom of a pocket 99 formed in the casing '52.

The casing 92 has an inlet chamber 11i-tl in communication with the vanes 97 located on the same side of the casing as the chamber 1139, and the casing 92 has an outlet chamber 191 in communication with the vanes 97 on the opposite side. An inlet conduit 132 is connected to the chamber i?, and outlet or line pressure supply conduits 103 and 1114 are connected to the chamber 101. The cavity 93 has a conduit 165 connected to it at its upper end and has a conduit 1116 connected to it at its lower end.

The pressure regulating valve S2 functions in conjunction with the pump 7S for causing the regulation of the output pressure of the pump 75 in the chamber 191 to predetermined values. The valve 82 comprises a casing portion 167 having ports 108, 199, 110, 111, 112 and 113, all opening into a cylindrical cavity 114 in the casing portion 107. A piston 115 is slidably disposed in the cavity 114 and is provided with an internal -cavity 115 in communication with ports 117 extending through the valve piston. An annular groove 118 is provided about the piston 115.

A plug 119 is provided in the upper end of the cavity 114. The plug 119 is provided with ports 121i in cornmunication with the port 112 and cylindrical connected cavities 121 and 122. The cavity 121 is in communication with the ports 121i, and the cavity 122 receives a piston 123 having a stein 124 adapted to bear on the piston 115. A compression spring 125 extends between the plug 119 and the piston 115.

ri'he port 1% is connected with the conduit 1113; the port 1199 is connected with the conduit 166; the port 11@ is connected with the conduit 195; the port 112 is connected with a conduit 126; and the ports 111 and 113 are bleed ports which, like all other bleed ports in the transmission controls, are adapted to freely discharge into the oil sump 127.

The selector valve 77 comprises a casing portion 123 provided with ports 129, 131i, 131, 132, 133, 134 and 135. rIhe casing portion is provided with a cylindrical cavity 136 therein in which a piston 137 is slidably disposed. The piston 137 is formed with an annular groove 15S and annular indentations 139, 149, 141, 142, 143, 144 and 145. Detcnt balls 146 acted on by springs 147 are adapted to fit in the indentations 139, 140, 141, 142', 143, 144.1 and 145 for yieldably holding the piston 137 in its 195, 1)4, 3, "2, 1, N and R positions, which correspond to 5th speed automatic range, 4th speed automatic range, 3rd speed, 2nd speed, 1st speed, neutral, and reverse, respectively.

The port 129 is connected with the conduit 126; the port 136 is connected with the conduit 103; the port 131 is connected with a conduit 14S; the port 132 is connected with a conduit 149; the port 133 is connected with a conduit 151); one of the ports 134 is connected with a conduit 151 and the other of the ports 134 is connected with a conduit 152; and the port 135 is connected with a conduit 153.

The coupling valve 83 comprises a casing portion 154 having ports 155, 156, 157, 158 and 159 therein. The casing portion is provided with a cylindrical cavity 169, and a piston 161 is slidably disposed in the cavity. The piston 151 has an annular groove 162 and is acted on by a spring 163 disposed between the piston 161 and a plug 161' fixed to close the lower end of the cavity 16?.

Both ports and 156 are restricted; however, the port 156 is smaller in diameter than is the port 155, and both ports are connected to a conduit 165 constituting the inlet conduit for the fluid coupling 26. The port 157 is connected by means of branch conduit 166 With the conduit 126, and the port 153 is connected to the conduit 194. The port 159 is a bleed port.

rIhe fluid coupling 26 has an outlet conduit 167 connected with a cooler 16S. The cooler 168 comprises a Water jacket 169 having a water inlet port 17@ and a Water outlet port 171. A cooling coil 172 is disposed in the water jacket 169 and is connected with the conduit 167. The coil 172 on its lower end is connected with an outlet 173 adapted to discharge into the sump 127.

A shunting conduit 174 connects the outlet 173 with the conduit 167, and a bypass valve 175 is provided in the conduit 174. The valve 175 comprises a ball 176 adapted to rest on a seat 177 and acted on and held on the seat by a compressionV spring 17S. A bi-metallic 7 strip 179 acts on the ball 1761and moves the ballV 176 off its seat 177 against the action of the spring 178 -when theoil in the conduit 167 is relatively cold.

The lubrication Valve 91 comprises a casing portion 180 having ports 181, 182, 183, 184, 185 and 1,86 therein. The casing portion is provided with a cylindrical cavity 187 therein, and two hollow pistons 188 and 189 are slidably disposedY in the cavity 187, A relatively strong compression spring 190 is disposed in the piston 188 and tends to move the piston 188 to the right, and a relatively weak compression spring` 191'is disposed in the piston 189 and tends to move therpiston 1897to the left. A stop 192 is provided extending between the ports 183 and 184 Yfor limiting the movement of the pistons 188 and 189'due to the action of their respective springs 190 and 191.

The port 18.1 is a bleed port; the ports 182, 183 and 185 are all connected with a conduit 193 which is a lubrication conduit connected with various parts of the planetary gear sets 27 and 28 requiring lubrication; the port 184 is connected by means of a conduit 194 with the line pressuresupply conduit 103; and the port 186 is connected by means of a branch conduit 195 with the conduit 126. It'will be noted that the ports 183, 182 and 185 are relatively restricted in cross-sectional size. The port 183 is relatively small, and the port 185 is relatively large, `although still restricted relative to the -cross-sectional sizes of the conduits used in the transmission controls. The port 182 is intermediate in crosssectional size between the ports 183 and 185, ports of these sizesY being provided for purposes which vwill hereinafter be described.

The modulator valve 81 comprises a casing portion 196 having ports 197, 198 and 199 therein connected with a cylindrical cavity 200. A piston 201 is slidably disposed in the cavity 200 and is provided with a groove 202. The piston 201 is hollow on its upper end, and a compression spring 203 is disposed in the piston and acts between it and the upper end of thecavity 200. The port 197 is a bleed port; the port 198l is connected with a conduit 204; and the. port 199 is .connected to the conduit 103 by means of a branch conduit 205. A restricted passage 206 is connected between the two ports 198 and 199.

The modulator valve 81 is controlled by means of a vacuum'motor 207 connected with the fuel intake manif fold 208 of the vehicle engine, The motor 207 com? prises a casing 209 having a flexible diaphragm 210 fixed at its periphery with respect to the casing 209 and movable therein ,and having a rigid piston 211 xed thereto by means of which it acts on the valve piston 201. Acompression spring 212V is provided in the housing.209 vand acts on the piston 211, tending to move it and the valve piston 201 upwardly as seen in the drawing. The housing 209 is connected with the manifold 208, as shown, so that the vacuum in the manifold 208 is impressed on the lower side of the diaphragm 210.

The rear pump 76 is adapted at times to supply iuid under pressure to the conduit 204 through the push start valve 80. The rear pump 76 comprises a pump casingY 213 having a uid inlet cavity 214 and a fluid outlet cavity 215. A gear 216 is in mesh with a ring gear 217 which is rotatably disposed in the casing 213 and is eccentrically located withrespect to the gear 216.

A segmental casing portion 218. is disposed between the gears 216 .and 2'17 and between the inlet and outlet cavif ties 214 and 215. The pump functions, when the gears 216y and 217 rotate inV their illustrated direction to carry uid between the gear teeth across the faces of the segmental casing portion 218 so as to transfer fluid from the inlet cavity 214 to the outlet cavity 215. The pump 7,6 is of conventional construction, and no further details of construction'and operation are deemed necessary.

The inlet cavity 214 is connected by means of a conduit 219 Withlthe sump 127,- and the outlet cavity 215 is 'i'.zonne'ctedl to a conduit 220. The conduit'220y is provided with a restricted bleed opening 221 for lubricating certain parts hereinafter to be described and also for relieving pressure within the outlet conduit 220 for purposes to be later mentioned. The gear 216 of the pump V76 is driven from the shaft 21 by anysuitable driving mechanism. Y

The push start valve 80 comprises a casing portion 222 having ports 223, 224, 225, 226 andY 227 therein. The casing portion 222 has an internal cylindrical cavity 228 inV which a valve piston 229 is slidably disposed. The piston 229 is provided with a groove 230, and the piston is hollow on its lower end to receive a compression spring 231 acting between the lower end of the cavity 22S and the piston 229.'

The port 223 is a bleed port; the port224 is connected with a conduit 232; the port 225 is connected with the conduit 220; the port 226 is connected with the conduit 204; and the port 227 is connected by means of a branch conduit 233 with the conduit 103.

The downshift inhibitor valve 79 comprises a casing portion 234 having ports 235, 236, 237, 238, 239, 240, 241, 242, 243, 244, 245, 246 and 247. The casing portion is provided with a cylindrical cavity 248 therein, and a valve piston 249 is slidably disposedV in the cavity 248. The piston 249 is provided with a peripheral groove 250 and is hollow at its right end'to receive a compression spring 251 extending between the right end of the cavity 248 and the inner end of the hollow space in the piston 249.

The port 235 is connected with the conduit 232, and the port 236 is connected with the conduit 232 through a restriction 252. An inhibitor regulator screw 253 is adjustable toward and away from a seat 254 which is connected with the port 236 and more or less opens a bleed port 255 with respect to the port 236. The ports 237, 238 and 239 are restricted bleed ports, discharging into the sump 127. The port 240 is a bleed port but is relatively unrestricted; The port 241 is connected by means of a conduit 256 with the port 198 of the modulator valve 81 which functions as a port supplying line pressure, subject, however, transiently on initialincrease, to the modulator valve 81, as will be described. The por-ts 242, 243, 244, 245 and 246 are respectively connectedwith con-V duits 257, 258, 259, 260 and 261. The port 247 is a bleed port.

The brake 30 is engaged by means of a hydraulic servomotor 262 which is also co-nnected with the line pressure port 198 of the modulator valveA 81, the connection being by means of a conduit 263. The servomotor 262 comprises a piston 264 slidably disposed in a cylindrical cavity 265 provided in a housing 266. A compression springv 267 is disposed between an end of the housing'266 tending to move the piston 264 to the left. The piston 264 is provided with a piston rodv 268 slidably extending through the housing 266, and the piston rod 268 is connected by means of a strut 269 with one end of the brake band 48, restingin a slot 270 provided in the end of the band. The other end of the band 48 is held by an anchor pin 271 iixed with respect to the casing 52 of the transmission, a strut 272 extending between the pin 271 and a notch 270a provided in the other end of the band 48. A compression. spring 273 is provided between outwardly extending ange portions 274 of the band 48 for yieldably holding Vthe band disengaged with respect to its drum.

' The housing 266 has brake apply chamber' 266g on the left side of the piston 264 and a brake disapply chamber 266i) on the right side of the piston 264. YThe housing is provided with a port 275 connected with the conduit 263 by means of which fluid under pressure may be supplied to the chamber 266g, and the housing 266 is provided with a po-rt 276 connected with a conduit 277 by means of which fluid under pressure may be supplied to the chamber 266b for assisting the springs 267 and 273 to disapply the band 43 with respect to, itsY drum.l

A bypass valve 273 (for details of construction see Figure 7) is provided for at times hydraulically connecting the chambers 266@ and 2565. The valve 27S comprises a piston 279 slidably disposed in a cylindrical cavity provided in the housing 266 and connected ou one end with the chamber 256i) and on the other end with the chamber 26651. The piston 279 is hollow, and a compression spring 231 is provided in the piston 279 and acts between the piston and a part of the housing 266, tending to move the piston 279 to the left. The piston 279 is provided with a port 232 therethrough which, when the piston is in its extreme left position, connects the chamber 26641 with the chamber 266b.

The brakes 31 and 32 each have similar brake applying and disapplying mechanism including a servomotor 262. For purposes of differentiation, the servomotor for the brane 32 is designated as 262A and its two ports as 275A and 276A, and the servomotor for the brake' 31 is designated as 252B and its ports as 275B and 276B.

The reverse interlock valve 85.- is connected with the line pressure supply port 133 of. the modulator valve 81 by means of a conduit 233. ll`he reverse interlock valve comprises a casing portion 284 having ports 285, 236, 287, 23S and 23e. The casing portion has a cylindrical cavity 293, and a valve piston 231 is slidably disposed therein. The piston 231 has a peripheral groove 292 and is hollow on one end to receive a compression spring 293 which acts between the piston and the right end of the cavity 293 to urge the piston 231 to the left.

port 235 is connected by means of a branch conduit with the conduit 126; the port 286 is connected to a conduit 235; the port 237 is connected to a conduit 2943; the port 233 is connected to the conduit 283; and the port 239 is connected to the conduit 257.

The freewheel valve 35 is also connected to the line pressure supp y port 193 of the modulator valve S1, the connection being by means of the conduit 263 and a conduit 297. The free-wheel valve comprises a casing portion 233 having a plurality of ports 299, 33u, 391, 332 and The casing portion has a cylindrical cavity 334 therein and a piston 355 is slidably disposed in the cavity 36d. The piston is provided with a peripheral groove 356, and the piston is hollow on one end for receiving a compression spring 397 which urges the piston 3135 to the limit of its movement to the left.

The port 299 is connected to a conduit 338; the port 330 is connected to a conduit 339; the port 391 is connected to the conduit 277; the port 3432 is connected to the conduit 297; and the port 363 is a bleed port.

The governor valve 7S is connected to the conduit 151 which in turn is connected to the selector valve 77. The governor valve 78 comprises a casing portion 310 having ports 311i, 312, 313, 314, 315, 316 and 317 therein. The casing portion 31) is provided with a cylindrical cavity 313 therein in which a piston 319 is slidably disposed. The valve piston 319 is provided with peripheral grooves 32@ and 321i, and the groove 321 is connected by means of a port 322 `and a passage 323 with one end of the piston 319. The port 311 is connected with a conduit 324; the port 312 is connected with a conduit 325; the port 313 is connected with a conduit 326; and the port 314 is connected to the conduit 151.

The valve piston 319 is moved by means of a speed responsive governor 327 which comprises a pair of ilyweight 323 each connected by links 329 between an arm 33t) integral with the piston 319 and a movable part 331. A compression spring 332 is disposed between the arm 339 and the part 331. As will be apparent, the weights 328 through the links 329 pull the piston 319 toward the part 331 against the action of the spring 332 as the velocity of the weights 328 increases. The part 331 may be moved along the axis of rotation of the weights 32S by means of the vehicle accelerator 333. The accelerator is connected by means of a link 334 with a bell crank 335 which is connected by means of a link 336 with the part 331. As an analysis of the linkage connecting the accelerator 333 and the part 331 will indicate, when the accelerator 333 is moved downwardly in a throttle opening direction, it will cause movement of the part 331 toward the part 33t) and thus tend to move the part 33d and the valve piston 319 to the left, assuming that the weights 32S remain away from their axis of rotation the same amount with no'change in speed of the weights. The Weights 328 are driven from the driven shaft 21 by any suitable mechanism, so that they are in effect, along with the spring 332, a governor responsive to the speed of rotation of the shaft 21.

Three needle pistons 337, 333 and 339 are slidably disposed in the casing portion 310 and are adapted to contact and be eective on the arm 330. The pistons 337, and 339 are respectively in communication with the ports 3i5, 3M and 317, so that fluid pressure in these ports is effective to move the pistons into contact with the part 33t?.

The second speed valve 86 is connected with the downshift inhibitor valve 79 by means of the conduit 25S and is connected with the line pressure supply port 198 of the modulator valve S1 by means of the conduit 263 and a conduit 345i. The second speed valve 86 comprises a casing portion 341 having ports 342, 343, 344, 345, 346, 347, 348, 349 and 359 therein. The casing portion 341 has a cylindrical cavity 351 therein, and valve pistons 352 and 353 are slidably disposed in the cavity 351. The piston 352 is in the form of a simple plug, and the piston 353 is provided with a pair of separated grooves 354 and 355. The piston 353 is hollow on one end to receive a compression spring 356 which acts to move the valve piston 353 to the left.

The ports 342 and 243 are connected by means of a conduit 357; the port 3453 is connected to the conduit 149; the port 344 is a bleed port; the port 345 is connected by means of a conduit 353 with the port 276A of the servomotor 262A and by means of a conduit 359 also with the port 275B of the servomotor 2&2B; the port 346 is connected with the `conduit 346; the port 347 is a bleed port; the port 349 is connected to the conduit 258; and the port 350 is a bleed port.

The fourth speed valve 8S is connected with the downshift inhibitor valve 79 by means of the conduit 260, with the governor valve by means of the conduit 325, and with the line pressure supply port 198 of the modulator valve 31 by means of the conduit 263 and a conduit 353. The valve 83 comprises alcasing portion 361 provided with ports 362, 363, 364, 365, 366, 367, 368, 369, 37d, 371, 372 and 373. The casing portion is provided with a cylindrical cavity 374.-, and pistons 375 and 376 are slidably disposed in the cavity 37d. The piston 375 is simply a plug, and the piston 376 is relatively elongated and is provided with grooves 377, 378 and 379. The piston 376 is hollow on one end to receive a compression spring 33@ which tends to move the piston 376 to the limit of its movement to the left.

The ports 362 and 371 are connected by means of a conduit 381; one of the ports 363 is connected with the conduit 152 and the other port 363 is connected with the conduit 398; the port 364 is connected with the conduit 296; the port 365 is connected with a conduit 382 and thereby with the clutch piston 69 of the clutch 3d; one port 366 is connected with a conduit 333 and the other port 366 is connected with conduits 334. and 335; the port 367 is a bleed por-t which is relatively restricted in cross-sectional size; one of the ports 363 is connected with a conduit 336 and the other of the ports 363 is connected by means of a conduit 337 with the clutch piston 55 of the clutch 33; the port 369 is connected with the conduit 363; the port 370 is a bleed port; the port 372 is connected with the conduit 269; and the port 373 is connected with the conduit 325.

A jet valve 38S is provided in the conduit 385 which is connected to the port 276B of the servomotor 262B.

Thej'e't valve comprises a restriction 389 in'the conduit 385and a conduit 390 in parallel with the restriction. A ball checkvalve is in the conduit 390 and comprises a ball 391 adapted to rest on a seat 392.

vThe iluid under pressure Within the conduits 382 and 387 is respectively applied to the pistons 60 and 55 for the clutches 3'4 and 33, `and ball check valves are provided ineconnection with the pistons which close on uid pressure application. The check`valve for each of the clutches comprises a'ball 393 adapted to rest on a seat 394 and thereby close aniopening 395 which may drain the iiuid pressure from behind the pistons 68 and- 55. The ball 393 will close the passage 395 when pressure is applied to the respective pistons 68 or 55; however, after uid pressure is released from the piston, the ball will .move olf its'seat 394 and permit the substantially complete `draining of the chamber behind the piston, so that iiuid pressure 'cannot build up Vin the chamber due to centrifugal force. Y

The iifth speed valve 89 is connected with the downshift .inhibitor valve 79 by means of the conduit 261, with the governor Vvalve v78 by means'of the conduit 326 and with the line pressure supplyrport 198 of the modulator valve 81 by means of the conduit 263 and a Conduit 396. The iifth speed valve comprises a casing portion 397 having ports 398, 399,400, 401, 482, 403, 464, 485 and 496. The casing portion 397 is provided with a cylindrical cavity 407, and valve pistons 488 and 409 are slidably disposed in'th'e cavity 407. The piston 493 is simply a slidable plug, and the piston 409 is relatively elongated and has peripheral grooves 410 and 411. The piston 489 is hollow on one end to receive a cornpression spring 412 jwhich functions to yieldablyv hold the piston 489V to the limit of its movement to the left.

The port 398 is connected by means of a conduit 413 with the port V404; the port 399 is connected to the conduit 153; the port 468 is connected to a conduit 414; the port 481 is connected to the conduit 384; the port 462 is connected to the conduit 396; the port 403 is a bleed port; the port 405 'is connected to the conduit 261; and

. the port 486 is connected to the conduit 326.

The 5-4 shift valve 90 comprises a casing portion 415 provided with ports 416, 417, 418, 419, 420, 421, 422 and 423. The casing portion 415 is provided with a cylindrical cavity 424 in which valve pistons 425 land 426 are slidably disposed. The piston 425 is simply a plug, and the piston 426 is relatively elongated Vand is provided With a pair of peripheralrgrooves 427 and 428. The piston 426 is hollow on one Yend to receive a compression spring 429 which holds the piston 426'yieldably to the limit of its movement tothe left.

The port 416 is connected'with the conduit 383; the port 417 is connected by means of a conduit 430 with the port 421; the port 418 is connected with the conduit 414; fthe port 419 is la restricted bleed port connected at all times with the port 418; the port 420 is an unrestricted bleed port; the port 422 is connected with the conduit 386; and the port 423 is an unrestricted bleed port.

The third speed valve 87, like the valves 88 and 89, is connected to the downshift inhibitor valve, the governor valve and the line pressure supply port 198 of the modulator valve 81. The connection to the governor valve is by means of lthe conduit 324; the connection to the downshit inhibitor valve is by means of a conduit 259; and the co-nnection to the port 198 of the valve S1 is by means of a conduit 431 and the conduit 263. The valve 87 comprises aV casingY portion 432Y having ports 433, 434, 435, `436, 437, 438, 439, 440, 441 and 442. The casing portion 432 is provided with a cylindrical cavity 443, and valve pistons 444 and 445 are slidably disposed in the cavity 443. The piston 444 simply constitutes a plug, and the piston 445 is relatively elongated land is provided with peripheral `grooves 446 and 447. The piston 445 is hollow on one end to receive a compres'- 12 sion spring 448 whichurges the piston 445 to the limit of its movement to the left. Y Y

The port 433 is connected to the port 440 by means of a conduit 449; the port 434 is connected to the conduit 150; the port `435 is a bleed port; theV port 436 is connected to the conduit 309; the port 437 is connected to the conduit'295; the port 438 is connected to the conduit 431; the port 439 is a bleed port; the port 441 is connected to the conduit 259; and the port 442 is connected to the conduit 324.

A modulator valve 450 is disposed in the conduit 295 and comprises a casing portion 451 in which a hollow cartridge 452 is slidably disposed. VThe cartridge on one end is provided with an opening 453 therethrough, and a ball 454 is adapted to rest on a seat 455 and close the opening 453. A spring 456 is provided in the cartridge 452 and holds the ball 454 yieldably on its seat 455. The cartridge 452 is also provided with side openings 457 therethrough which are closed at times bythe casing portion 451 depending on the position of the cartridge 452 in the casing portion 451. As will be observed, one end of the casing portion 451 is connected with the port 437 of the third speed valve 87, and the other end is connected with the port '286 of the reverse interlock valve 84.

In operation, the setting of the selector valve 77 determines the speed ratio that exists in the transmission. When the piston 137 yof this valve is in its R, 1, 2 or 3 positions; reverse drive, low gear drive, second gear drive, or third gear drive are provided by the transmission exclusive of any of the other drives. When the piston 137 is in its N position, the transmission is in neutral. When the piston 137 is in its D4 position, the controls are in one of their `automatic ranges in which the transmission starts'in second speed, changes to third speed and nally changes to fourth speed. When the piston 137 is in its D5 position, the transmission automatically starts in lsecond speed, changes to third speed, thereafter changes to fourth speed, and :finally changes to iifth speed.

When the piston 137 is in its N position, fluid under pressure exists in the groove 138 and pont 130 of the selector valve, but the'groove V138 is out of communication with the other ports. Line pressure also exists in the port 198 of the modulator valve 81, and this line pressure is supplied through conduit 256 to the inhibitor Valve 79, through conduit 396 to the fifth speed valve 89, through conduit 360 to the fourth speed valve 88, through conduit 340 to the second speed valve 86, through conduit 297 to lthe freewheel valve and through conduit 431 to the third speed valve 87; however, each of these Valves 'in this condition of the controls simply blocks this line pressure, and it is of no effect.

The'port 198 of the modulatorY valve 81 is also connected by -means of the conduit 263 with the port 275 of the servomotor 262 for the brake 30, and line pressure is supplied to the cavity 266a of the servomotor 262 and moves the'piston 26'4 against the Springs 267 and 273 to engage the brake 30.Y A power train is thus completed through Ythe rst planetary gear set 27; however, since none of the friction 'elements of the second planetary gear set 28 is engaged, the transmission is as a whole in lneutral, and theY driven shaft'21 is not driven. The ring gear 67 connected with the carrier 40 of the iirst planetary gear set 27 is, however, driven, so that power may -be derived from the power takefof gear 68 movable yinto mesh with the gear 67. The valve 278 in the Servomotore2'62 under these conditions is closed. The pressure in the cavity 266x: moves the piston 279 against the action of the spring 281 so as to close the port 282 in the piston 279 by means of the walls of the surrounding cavity 280, and pressure thus cannot Vleak throughY the Yvak/e278 to thecavity 266b in the servomotor 262.

The line pressure -applied to the selectorvalve 77 vand that existing in' the kport .198 of the modulator valve '31 is derived from the front pump 75 driven by the drive shaft 2i) of the transmission. The rotor 96 of the pump 75 is driven by the drive shaft in the illustrated direction, and the vanes 97 in contact with the cylindrical cavity 95 function to draw fluid from the inlet cavity 169 in the pump casing 92 and discharge it into the outlet cavity 101 in the casing 92. Fluid is pumped by the pump 75 through the conduit 162 from the sump 127, and uid output from the pump is present in conduits and 104. The conduit 103 is connected with the elector valve 77 for supplying line pressure thereto, and the port 198 is connected through the restriction 296 and branch conduit 295 with the line pressure supply conduit so that line pressure exists in the port 198. The modulator valve 81 functions to bypass at times the restriction 296 to connect the conduits 103 and 295 with the port 198. The diaphragm 210 of the vacuum motor 297 for controlling the valve piston 291 of the modulator valve 81 has the vacuum of the manifold 298 of the vehicle engine applied thereto, and thus when there is little torque demand and the vehicle accelerator 333 is released, there is a relatively high vacuum, and the piston 2111 is moved downwardly due to the action f the spring 203 to block the port 198 with respect to the port 199 and branch conduit 295. The high vacuum is eective on the diaphragm 210 drawing the diaphragm 21o and the piston 211 downwardly against the action of the spring 212, allowing such action of the spring 203 moving the piston 261 downwardly; conversely, when the vacuum in the manifold 298 is low, as when there is relatively large torque demand by the vehicle operator and the engine throttle is open, the spring 212 in this case is eective through the piston 211 to move the valve piston 291 upwardly against the action of the spring 263 to connect the ports 199 and 193 through the groove 262. l/Vhen the restriction 266 is effective, as when the accelerator is released, it impedes the flow of fluid from the branch conduit 2635 to the port 198 so as to impede the flow of iluid to any of the parts which may be connected with the port 193, but when the vacuum is relatively low with an opening of the vehicle throttle, there is no such impedance to fluid flow, and fluid pressure is applied instantaneously to any of the parts that may be connected with the port 19S. 1n either case, the pressure in port 193 rises to full line pressure that em'sts in conduit 193 when the iiuid flow through the restriction 296 ceases.

The pressure regulator valve S2 functions to regulate the pressure output of the pump 75 to a predetermined value, such as 8O lbs. p.s.i. 115 is at the limit of its movement downwardly under the action of the spring 125 so that its ports 117 are in communication with the port 199, and any fluid pressure from the pump 75 is transmitted to the lower part of the cavity 93 in the pump housing 92, augmenting the action of the spring 98 in holding the pump casing 9din its illustrated position in which there is maximum eccentricity between the casing 94 and the rotor 96 and a consequent maximum pumping action. As the pressure in the conduit 1133 increases, it is effective against the piston 115 to move the piston upwardly against the action of the spring 125 to connect the ports 117 with the port 11@ and supply uid under pressure from the conduit 193 through the conduit 105 to the upper end of the cavity 95 in the pump casing 92. At the same time, the conduit 195 and port 1139 are connected through the groove 11S with bleed port 113 to relieve the fluid beneath the pump casing 94. The huid under pressure in the conduit 105 acts on the upper surface of the pump casing and moves it downwardly against the action of the spring 93 to thereby reduce the eccentricity between the rotor 96 and the cylindrical cavity 95 and reduce pumping action by the pump 75. As pressure in the conduit 163 reduces for any reason, the valve piston 115 moves downwardly to connect the ports Initially, the valve piston V 14 Y 117 with the port 109 while if the pressure in the con duit 163 tends to become too great, the piston 115 moves in the opposite direction connecting, as has just been described, the ports 117 with the port 119, for supplying fluid under pressure either to the bottom or the top of the cavity 93 respectively. The net result of the action of the piston is to cause the pressure in the conduit 103 to remain substantially the same at a preselected line pressure, for example 80 lbs. p.s.i.

Line pressure in the conduit 1% is transmitted through the branch conduit 233 to the upper end of the piston 229 of the push start valve 80. rl`he piston 229 is thus moved downwardly against the action ot the spring 231, so that the port 226 and the conduit 294i are blocked by the piston 229. rEhe groove 23@ of the piston 229 under these conditions connects the ports 225 and 224 for purposes hereinafter to be described.

Fluid is supplied to the iiuid coupling 26 in neutral and all forward drives through the two restricted ports and 156. The piston 161 of the valve 33 is in its uppermost position, due to the action of the spring 163, and the groove 162 of the piston 161 connects the ports 158, 155 and 156. Fluid ows from the conduit 104 connected with the output cavity 191 of the pump 75, through the valve 83 and its restricted ports 155 and 15o to the inlet conduit 165 of the fluid coupling'26. Fluid ows out of the coupling 25 through the conduit 167 and through the coil 172 in the oil cooler 168 to the outlet 173 and from thence into the sump 127. Cooling water is made to flow through the housing 169 of the cooler from the port 179 to the port 171, and the oil iiowing through the coil 172 is thus cooled. The ball 176 of the bypass valve under cold oil conditions is 0E its seat 177 and allows oil from the conduit 167 to bypass the cooler 169 through the bypass conduit 174. The bimetallic thermostatic element 179 under cold oil conditions acts `against the ball 176 and moves it oif its seat 177 against the action of the spring 17S in order to secure this result. Upon subsequent heating of the oil, the end of the bimetallic thermostatic element 179 moves upwardly allowing the ball 17o to move on its seat 177 and block the conduit 174. u

The lubrication valve 91 provides a connection between the ports and 183 when both of the pistons 188 and 189 are `at the limits of their movement against the stop 192 under the action of the springs 199 and 199. The port 133 is relatively restricted and provides a minimum flow of lubricating iluid to the gear sets 27 and 2S under idling conditions of the vehicle engine, when the line pressure in the conduit 163 and connected conduit 194 is substantially less than the pressure ordinarily maintained by the pressure regulating valve S2. When the pressure in the conduits 193 `and 194 rises to that line pressure maintained by the valve 82, for example, 80 lbs. p.s.i., this pressure exerted on the left end of the valve piston 139 moves the valve piston to the iight against the action of its spring 191 and opens the relatively large port 1555 with respect to the port 184 and provides a greater flow of lubricating Huid. The piston 183 does not move at this time but requires a much higher line pressure to move, such as ya pressure of lbs. p.s.i. which is used for reverse drive, as will hereinafter be described.

The piston 137 of the selector valve 77 is moved into its l or low speed position in order to obtain low speed drive through the transmission. With the piston 137 allowed to remain in its l position, the low speed drive through the transmission remains without change. The piston 137, when its l position, connects the ports 1243 and 131 by means of its groove 138, and fluid pressure is thus supplied from the line pressure conduit 193 to the conduit 1413 and the servomotor 262A, and particularly the apply cavity Zoon of this servomotor. The brake 32 is thus applied, and the brake 3l? remains applied since its servomotor 262 remains connected to the port 198 of the modulator valve S1. With both of the brakes and 32 applied,r-the low speed ratiol is completed through the transmission. i Y Y 'l As the vehicle speedincreases, the driven shaft pump 47,6 begins to pump iluid into the conduit` 220. The push-start valve piston 229,V as at all times When the front pump 75 is producing uid under pressure, is at its lowermost position connectingthe ports 225 and 224 by means of its groove 230, and the fluid pressure from the line 220- is Vsupplied to the conduitV 232 and to the left end of the downshift-inhibitor valve 79. As theV vehicle speedincreases in first speed ratio, the pressure. output of the driven shaft pump 76 increases and finally moves the piston 249 off the valve79 tothe rightV -against the action of the spring 251. Prior to such movement, the iluidout-k put of the pump 76 escapesthrough therestricted orifice 221, and lalso through the restrictedV orifice 252 andthe restriction foi-med by the inhibitor regulator screw 253. Due to these relief openings, the pressure in the conduits 4220 and 232 increases approximately coordinately with the speed of the driven shaft 21.. As thevalve piston 249 moves farther in low speed ratio,.it uncovers Vthe port 236 which shunts the restriction 252and this open# ing ofthe port 236 temporarily decreases the uid pres-V sure output of the pump 7 6 and prevents the valve piston 249 from moving farther yat this time.Y The speeds of the vehicleengine and thereby the vehicle in first speed ratio are, .of course, limited, and the valve piston 249 can only go to itsposition uncovering the port 236 .in this speed ratio. The screw v253 is adjustable with respect to its seat 254 to allow the response of the piston 249 tobe adjusted for diierent capacities of dierent pumps 76. The restricted Lb-leed orifice 221 may be allowedY to discharge directly into the sump 127 but is preferably used for lubricating moving parts .of the transmission', such as, lfor example, a gear drive for driving the governor. 327 from the driven shaft 21. i

The piston 249 in moving to uncover the port 236 connects the port 242 with the port 241. The port .241 is connected by means of the conduit 256 with the line pressure supply port 198 ofthe modulator valve 81,. and line. pressure is thus supplied to the reverseV interlock valve 84 through the conduit 257 connected to 'the port y second speed ratio by moving the selector valve piston 16 32 aretetfective to disengage'the brake.4 lll/'hen` the brake 3 1 is 'engaged and the brake 32 is disengaged, with the brake VSil'allowed to remainengaged,.the transmission is in second speed forward drive.A I i j As has been noted, the port 346 of thesecond Yspeed valve 86 through whichV pressure Yis .applied to Ythe apply side Vof thek piston 264 of theA servomotor262B Ifor the brake 31 is connected with the; line pressure.. supply port 19.8 of the. modulator valve 871V. instead `of directly with the line pressure supply conduit 103, and the application of line pressure to thev servomotor 262B for engaging the brake 31 is thus underthe control of theV modulator Vvalve 8,1. Assuming that the selector valverpiston 137Vis moved from its l to itsrf2ltpositionvvhen theA accelerator 333 is `released in a closedrthrottleV position, in this case; the vacuum motor 207 is Aeifectiver'due to the highvacuum` then present in the manifold 208, to allow the spring 203 effective on the pistonf201 of themodulator valve 81 to move Ythe piston 291 into position closingVV the port 198 with respect to the port ,199. Under these conditions, the flow of fluid pressure Yto the port 346 of the second speed valve 86 is restricted bythe restriction ,206 associated with Vthe `modulatorfvalve Y81,'and'the fluid pressurein the apply cavity 266a'of the'servomotor 262B builds up slowly due to the restriction 206and the completion of the second speed power train takes place relatively slowly so that an undesirable jerk upon completion of this power train by engagement of the brake 31 -does not take place. If the selector valve piston k137 Yis moved fromY its 1`to its 2 position whenfthe vehicle engine is transmitting substantialY torque ,withV the accelerator depressed, the vacuum in the manifold 208 Will beY relatively low, and the spring 212 inthe vacuum motor 207 will move thevalve piston 201 of the modulator valve 81 upwardlyso as to connect the ports 199 and 198 through the groove 202 of the piston 20,1. Under these conditions, there will be no such restricted flow of Huid pressure to the port 346 of the second speed valve 86, and a relatively rapid engagement of the brake 31 Will take place. Since the torque output of the vehicle engine at this time is relatively high, a relatively rapid engagement of the brake 31 may take place Vwithout an undesirable lurch of the vehicle. It Will be noted that the disapply cavity 2661i ofthe servomotor 262A for the brake 32 is Vco'nnected'in parallel With the supplyY cavity 266e of the servomotor 262B for the brake 31- so that the disengaging action of the brake 32 is coextensive with the engaging action ofthe brake 31,

Y and the brake 32 will disengage either fast or slow e0- 137 into its 2 position, and with the piston 137 VVremaining in this position, the transmission will remain in second speed ratio. When the piston 137 is in its 2 position, its groove 138 connects the ports 131i, 131 and 132. The port 131 supplies line pressure as in first speed ratio, to the cavity 266e: of the servomotor 262A. The port 132.t,hrough the conduit 149 supplies lines pressure to the. port 343 of the second speed valve 86, and the pist0n 353 of the valve 86 is moved-,to the iight against the action of its spring356, Vso as to connect the ports 345 and. 346. by means of the groove 354 in the piston 353 and to connect the po-rts348 and 349 by means of the piston groove 355. The port 346 is connected bvmeans of the conduit 340 and the conduit 2.63.with the line pressure supply port 198 of the modulator Valve81, and the line pressure is supplied through the-conduit 340, the port 346, the groove 354, the port 345, the Vconduit 358 and the .port 276e to thedisapply. cavity` 26617 of the servomotor 262A for the brake k32. YThe brake apply cavity 266i: .of the brake servomotor 262B is connected by means of the conduit 359 with the conduit 358, and line .pressure is simultaneously applied within this cavity so as t0 move the'piston 264 ofthe servomotor 262B in the engaging direction to engage the brake 31.. The fluid pressure in the cavity 266 b ofthe servomotor Y262A is effective to disengagethe brake 32, since the line pressure in this cavity 266!)V balances that inthe opposing v.cav ity`.266a, and thesprings 267` and 273 for the brake extensively with a fast or slow'engagement of the brake 31 in making this change of drive.

Various fluid leakages may be .expected to occur in a fluid system of the type illustrated and described.'V Due to these leakages, itV can be expected that perhaps'the line pressure in the disapply cavity 26611 is less than the line pressure in the apply cavity 266:: of the servomotor 262A for the brake 32 when second speed 'drive is completed. In order to prevent drag' of the brake'b'and 62 on its drum 61 due to such a differential i'n pressure, We have provided the valve 278 in the^servomotor 262A. The valve 278 operates,v when there Yis a relatively small diierential of pressure in the cavities 266b'V and 266az,A to open `and oonnect the cavities 26651 and 266b and assure that no such differential of pressure exists. When the pressureV in the disapply cavity 266b is'Withinl this small diiferential of pressure With respect to the pressure in the cavity 266a, the pressure in the cavity 266b is effective on the right side of the valve piston 279 and augments the Yaction ofthe spring 281V in moving the valve piston 279-to the limit of A its movement to therleftV so as to open the port 282 in the piston 279 with respectV to the cavity 266:1 and thereby connect the cavities `266:1 and 266b. The valves A278 in the other servomotorsk 262 and 262B, incidentally, operate in the Same manner to connect the disapply cavities 266!) and the apply cavities 266mm therrespective servomotors when there is a small differential in pressure'existing in ,the two cavities. In an actual embodiment, thisksmall 17 diierential of pressure may be on the order of l2 lbs. p.s.1.

The speed of the transmission driven shaft 21 and of the vehicle in second speed drive may become sufficient so that the pressure in the conduits 220 and 232 from the driven shaft pump 76 may be sufficiently high to move the valve piston 249 of the downshift inhibitor valve 79 one step farther to the right to vent the restricted port 237 with respect to the port 235 and to connect the port 243 with the port 241 by means of the groove 250 in the piston 249. The port 241 is supplied with line pressure from the port 19S of the modulator valve 81, and the port 243 supplies line pressure through the conduit 258 to th eport 349 of the second speed valve 36. When the piston 353 of the second speed valve 86 is at its eXtreme right hand position `as for second speed drive just described, its groove 355 connects the ports 349 and 343 and supplies line pressure through the conduit 357 to the port 342, and line pressure is thus applied on the left end of the plug 352. The plug 352 is effective to hold the piston 353 at the limit of its movement to the right, even if the selector valve piston 137 is moved back from its 2 position to its l position to drain the conduit 149 and connected port 343 of the second speed valve 86. Thus line pressure continues to exist in the conduits 358 and 359 for maintaining the transmission in second speed ratio even though the selector valve piston is moved back, assuming that the speed of the vehicle has become sufficient to move the downshift inhibitor valve piston 249 into its position in which its groove 256 connects the port 243 with the sport 241. Excessive increases in vehicle engine speed are thus avoided.

The transmission is changed from second speed ratio to third speed ratio by moving the selector valve piston 137 from its 2 to its 3 position, and in the latter position of the selector valve, no upshifts from third speed ratio can take place in the transmission. The selector valve piston 137 in its 3 position connects the ports 13), 131, 132 and 133 by means of its groove 138. Fluid pressure supplied to the ports 131 and 132 has the same effect as for the second speed drive just described, and the duid pressure supplied to the port 133 is eiective for causing the shift from second speed ratio to third speed ratio in the transmission. Fluid pressure supplied to the port 133 ows through the connected conduit 150 to the port 434 of the third speed valve 37 and moves the piston 445 to the limit of its movement to the right against the action of its spring 448. The valve piston 445 in this position connects the ports 44@ and 441 by means of the groove 447. The valve piston 445 in this shifted position also connects the ports 436, 437 and 43S. The port 438 is supplied with line pressure from the port 19S of the modulator valve 81, and iiuid pressure is thus supplied to both ports 436 and 437. The line pressure in port 436 flows through the conduit 309 to the port 300 of the freewheel valve S and thence through the groove 306, port 391, conduit 277, and port 276 of the servomotor 262 to the disapply cavity 266]) of the servomotor 262. Line pressure in this cavity causes the disengagement of the brake 30. rl`he line pressure supplied to the port 437 flows through the conduit 295, valve 459, the port 286, groove 292, port 287, conduit 296, the port 364 of the fourth speed valve 88, port 365, conduit 382 to the piston 60 of the clutch 34, thus applying the clutch. Since the supply port 438 of the third speed valve 87 is connected to the port 19S of the modulator valve S1, the engagement of the clutch 34 and the disengagement of the brake 3G is relatively protracted for released accelerator position and relatively quick for depressed accelerator position, due to the action of the modulator valve 81, as was described in connection with the change from rst to second speed drive. In addition, the valve 450 provides a modulating inuence on engagement of the clutch 34. The duid how to the clutch piston 60 takes place through the orice 453 and moves the ball 454 ot its 18 seat 455. The cartridge 452 is moved to the limit of its movement downwardly so that the openings 457 in the cartridge are closed, and all uid ow must take place through the orifice 453.

During the engagement period for the clutch 34, the valve 450 acts as a pressure reducing valve. The line pressure in the conduit 295 between the port 437 and valve 450 acts against the ball 454; and this force, after uid ows through the orifice 453, is balanced by the spring 456 and a reduced clutch engaging pressure in the conduit 295 between the valve 456 and the port 286.

During third speed drive, the transmission driven shaft 21 and the vehicle may be driven at suticient speeds so that the downshift inhibitor valve piston 249 is moved still another step to the right against the action of its spring 251, opening another restricted orifice 238 to the pump 76. The valve piston 249 at this time connects the port 244 in addition to the ports 243 and 242 with the line pressure supply port 241, and line pressure is supplied through the port 244 and connected conduit 259 to the port 441 of the third speed valve 87. When the valve piston 445 of the third speed valve has been shifted over to the limit of its movement to the right, it connects the port 441 by means of its groove 447 with the port 440 and thereby with the port 433 by means of the conduit 449. Line pressure is thus applied on the left end of the plug 44, and even though the selector valve piston 137 may be shifted back to a lower speed position, draining the conduit 150, pressure in which initially moved the piston 445 to the right; nevertheless, the piston 445 remains in its third speed position, and third speed drive remains effective. As Will be recognized, this action of the downshift inhibitor valve 79 on the third speed valve is similar to its action on the second speed valve 86, maintaining each valve in its shifted position, once shifting has taken place, so that the speed ratio through the transmission will not be reduced once a high speed of the vehicle has been attained at the high speed ratio, preventing excessive vehicle engine speed.

The selector valve piston 137 when moved another notch to the right is in its D4 position and so controls the transmission that the transmission starts in second speed ratio and changes automatically to third speed ratio and nally changes automatically into fourth speed ratio which is the highest ratio available in this range. The piston 137 in its D4 position connects the ports 13G, 131, 132, 133 and 134 together by means of the groove 138. Line pressure is thus supplied through a port 134 to the conduit 151. The governor valve piston 319 is initially in its position connecting the ports 311, 312, 313 and 314 by means of its groove 320, and line pressure is thus supplied to the conduits 324, 325 and 326 respectively connected with the rst three mentioned ports. The conduit 324 is connected with the port 442 of the third speed valve 87 and thus supplies line pressure to the right end of the valve piston 445. rIltis line pressure, together with the spring 448, hold the piston 445 to the limit of its movement to the left, even though line pressure is supplied from the port 133 and conduit 150 to the right end of the valve piston 445. The governor valve piston 319 is controlled in accordance with the speed of the driven shaft 21 of the vehicle, as is the downshift inhibitor valve 79, and it is assumed that the vehicle speed is so low that the downshift inhibitor valve piston 249 closes the port 244 with respect to line pressure port 241, and line pressure is not supplied to the left `end of the plug 444.

One of the ports 134 of the selector valve 77 is connected with the conduit 152, and line pressure is thus applied on the left end of the fourth speed shift valve piston 376 which would function to move the piston to the right against the action of its spring 380. Such shifting movement of the fourth speed valve piston 376 is prevented, however, at this time since the port 312 of the governor valve 78 is connected with the port 314,

376 sotlatthis line pressure together with the spring 380 function Yto hold the piston 376 from movement to the iight.

As has been previously explained, the transmission is shifted from'second speed torthird Vspeed by moving the third speedvvalve piston 445 to the limit of its movement to the right bythe application of fluid pressure through .the conduit 150 and Vport 434 on the leftend of the piston 445.V The pressure from the port 311 of the governor valve 78 transmitted through the conduit 324 to the right end of the valve piston 445, prevents the Vmovement of the piston 445 to the right and thus prevents third speed from being activated, with the selector'valverpiston 137 being in its D4 position. As will be hereinafter described, the piston 376 of the fourth speed valve 88 likewise, when shifted to the right against the action of its spring, causes an vupshift from third speed to fourth speed; however, with the selector valve piston 137 lbeing in its D4 position, line pressure is supplied Vfrom the governor valve port 312 through the conduit 325 to the right end of the 'piston 376 andV prevents its movement to the right, and

fourth speed ratio is likewise not completed.

Under these conditions, with' the governor valve piston in its Vposition bridging the ports 311, 312, 313 and 314 by its groove 320, the transmission is in second speed ratio, and a start of the vehicle is made in this ratio. The brakes 30 and 31 are engaged for completing this ratio'in the same manner as when the selector valve piston V137 is in its 2 position, and the second speed valve piston 353 is moved to its right hand position to supply line pressure to both the conduits 358 and 359. Although the second speed valve 86 is quite similiar to the third speed valve 87 and the fourth speed valve 88, it will be noted that the second speed valve 86V does not receive pressure from the governor valve 78, and the second speed vdve piston 353 is free to move to the right to its second speed completing position due to line pressure received from the selector valve 77.

Y The governor valve pistonV 319 is controlled both by the speed of the driven shaft 21 of the transmission and by the accelerator 333. The weights 328 are driven from the shaft 21 as previously described, and on increasing speeds of the shaft 21 and of the weights, they will draw the parts 330 and 331 together against the action of the spring 332, and assuming that the part 331 is stationary,

the valve piston 319 will be moved to the right. Actually,

the Vpart 331 moves along with the accelerator 333, and when the accelerator 333 is moved downwardly toward fully opened throttle position, it will cause' a clockwise rotation of the bellcrank 335 through the link 334 and will move the part 331 to the left through the link 336.

When the speed of the shaft 21 increases sufficiently, the Vpiston 319 is` moved to the right so as to bridge the ports 312, 313, 314 and 315 with the groove 320, and the port 311 is drained to the sump 127 through the open end of the cavity 318. The port 311 is connected through the conduit 324 with the port 442 for the third speed valve 87, yand thus the pressure effective on the right end of the third speed valve piston 445 is removed, and the line pressure effective on the left end of the valve piston 445 through the conduit 150 and port 434 is effective to move the piston 445 to the right to the limit of its movement, in which third speed forward drive is completed as hvas been previously described. In third speed forward drive,

the speed of the shaft 21 may be sufficient so as toV move the downshift inhibitor valve piston 249 sufficiently to open the port 244 with respect to the port 241, and the pressure owing through therport 244 is effective to prevent a movement of the third speed valvepiston 445 to the left in a downshifting direction as has been previously described. i

- When the governor valve piston 319 is Yin .its :third speed position as just described, line pressure is adrnitted to the vport 315-and is effective on lthe Ysm'allvpiston 337 to Ymove thepistonrinto contact with the movable part 330.V `'l`lie7pist'onv337 acts as a pressure means to apply anV additional force on ,theA part330`tending to hold it in ifS upshifted third speed position, once this position has been attained, yand Vcauses the speed of the governor 327 at which a downshifting movement of the piston 319 occurs to be substantially less than the speed at whichran upshifting movement occurs.V

When theV speedy of lthe driven shaft 21 of the transmission increasesrstill further sufficiently, the Igovernor valvepiston 319 is moved farther to the right so as to connect the ports 313, 314, 315 and 316 by means of the' groove '320, draining theF ports 311 and 312 to the sump 127 through the open end of the cavity 318. The port 312 is connected'by the conduit 325 with the port 373 of the fourth speed valve 88, and theline pressure previously effective on the right end of the fourth speed valve piston 376 is drained and allows the piston 376 to move to the right tothe limit of its movement under the eifect'of the line pressure impressed on the leftpend of the pistonV 376 through the' conduit 152 and port 363. The piston 376 in this position connects the portsk369 and V368. Line pressure from the modulator valve port 198 is supplied Vto the port 369 through the'conduit 360, and from thence line pressure flows through the groove 378 and conduit 387 to the piston 55 of the clutch 33 to engage the clutch. The modulator valve 81 is elfective to provide a restriction in this supply of line pressure to the clutch if the accelerator is in a released position. Line pressure is drained from the piston 60for'the other clutch 34 by thisV movement of the fourth speed valve piston 376, the flow of fluid from the piston 60 to the sump being through the Vconduit382, the port'365, the groove 377, the port 366, the conduit 384, the port 401 in the fth speed valve 89, the groove 410, the port 400, the conduit 414, the port 418 of the 5-4 shift valve 90, the groove 427 and the port'419. As has been previously noted, the port 419 is relatively restricted, and this is for the purpose of retarding the disengagement of the clutch 34 to assure that the other clutch 33 is engaged prior to disengagement ofthe clutch 34 so that there can be no complete breakage of the drive through the transmission.

Inv fourth speed ratio, the transmission is capable of driving the shaft 21 and the vehicle at such speed that the rear pump 76 provides such pressure as to move the downshift inhibitor valve piston 249 to the right so that all of the ports 236, 237, 238 and 239 are in communication with the port 235. The groove v250 at this time connects the ports 242, 243, 244 and 245 with the line pressure supply port 241, andY line pressure from the port 245 is supplied through the conduit 260 to the fourth speed valve 88, and particularly'to its port 372. Line pressure in port 372 ows through the groove 379of the fourth speed valvepiston 376, port V371, conduit 3811 and port 362 to the left endrof the plug 375. The application of line pressure to the plug of the fourth speed valve functions in the same manner as in the previously Y described valves, namely, to assure thatV the fourth speed valve piston cannot be moved to the left to a downshftng position, even though the selector valve piston 137 is moved into one of its previously described posiv tionsgcutting olf the supply of line pressure to the fourth speed valve through the conduit 152.2

VThe piston 338 'of the governor valve 78 is connected with the line pressure supplied from the port 314 in the fourth speed position of the piston 319, and this piston 338 functions 'similar to the piston 337 in yieldably holding the governor valve piston 319 in itsrupshifted position.

- The function of the freewheel valve is to eliminate the engagement of the brake 30 for the second speed drive with the selector valve 77 being in its D4 position. As has kbeen described, the selector valve piston 137 supplies line pressure through the port 363 in the D4 position of the piston 137, and this pressure is transmitted through the conduit 30S and port 299 to the left end of the freewheel valve piston 305. The piston '305 is thus moved to the limit of its movement to the right against the action of its spring 307 and connects the ports 302 and 301 by means of its groove 306. The port 302 is connected by means of the conduit 297 With the line pressure supply port 198 of the modulator valve 81, and line pressure is thus supplied through the ports 302 and 361, conduit 277 and port 276 to the disapply cavity 266b of the servomotor 262 for maintaining the brake 30 disengaged. A smoother ratio change from second to third or back again from third to second in the D4 range is obtained with the freewheel brake 29 effective in lieu of the brake 30 as the freewheel brake 29 automatically engages and disengages, depending upon the relative rotation between the inner and outer races of the brake 29.

The transmission controls are put in their D5 range by moving the selector valve piston 137 into its D5 position. In this range, the transmission starts in second speed drive, shifts automatically to third speed drive, thereafter shifts automatically to fourth speed drive, and finally shifts automatically to fifth speed drive.

When the selector valve piston 137 is in its D5 position, the groove 138 connects the port '135, along with the ports 131, 132, 133 and 134, with the line pressure supply port 130. Line pressure is thus supplied through the conduit 153 to the iifth speed valve 89 and is effective on the left end of the iifth speed valve piston 409 which tends to move this piston to the right to the limit of its movement against the action of its spring 412. Assuming, however, that the vehicle speed has not as yet attained a very high value, the fifth speed valve piston 409 remains to the limit of its movement to the left. When the governor valve 319 is in its illustrated position, it connects the line pressure supply port 314 with the port 313, as Well as the ports 311 and 312 previously discussed and line pressure is thus supplied through the port 313 and connected conduit 326 and port 406 to the right end of the fth speed valve piston 409, so that the line pressure augments the action of the spring 412 in holding the piston 409 to the limit of its movement to the left, even though line pressure is supplied through the conduit 153 in the D5 position of the selector valve piston :137 to the left end of the fifth speed valve piston 409.

The transmission is shifted from second speed drive to third speed drive and nally to fourth speed drive by movements of the governor valve piston 319 successively uncovering the ports 311 and 312, as has been previously described in connection with the D4 position of the selector valve piston 137. When the speed of the driven Shaft 21 increases stili further so that the governor valve piston 319, in addition, uncovers the port 313, the line pressure which has previously been in communication with the right end of the fifth speed valve piston 409 through the port 313 is now drained through the port 313, and the valve piston 409 is moved to the limit of its movement to the right against the action of its spring 412 by the line pressure effective through the port 399 on the left end of the piston 409. It should be noted that, even though the speed of the shaft 21 in the' D4 range reached the critical governor speed just described, nevertheiess, such a movement of the fifth speed valve piston 409 could not take place, in View of the fact 'that line pressure in the D4 range is not supplied to the left end of the fth speed valve piston 409 through the port 399 and conduit 153.

When the fifth speed valve piston 409 is at the limit of its movement to the right, it connects the ports 402 and 401 by means of the groove 410. Line pressure is sup-- plied from the line pressure supply port 198 of the modulator valve 81 through the conduit 396, the port 402, the port 401 and the conduit 384 to the uppermost port 366 22 of the fourth speed valve 88. The line pressure in the conduit 385 connected with the conduit 334 ows through the restriction 389 to the disapply cavity 266]; of the servomotor 262B for the brake 31, and the brake 31 is thus disengaged, although, due to the existence of the restriction 389, the disengagement is relatively slow.

The fourth speed shift valve piston 376 is, at this time, at the limit of its movement to the right, since the transmission has previously changed into its fourth speed ratio, and line pressure from the port 366 ows through the groove 377 of the shift valve piston 376 to the port 365 and thence through the conduit 382 to the piston 60 for applying the clutch 34. The clutch 33 remains engaged as in fourth speed drive due to the fact that the fourth speed shift valve piston 376 remains in its upshifted position, to the limit of its movement to the right, and thus both the clutches 33 and 34 are engaged to complete the fth speed drive through the transmission.

The 5-4 shift valve is actuated at the same time as the clutch 34 is engaged for purposes hereinafter to be mentioned. The line pressure from the lower port 366 ows through the conduit 383 and port 416 to be effective on the left end of the plug 425 of the 5-4 shift valve 90 and move the pistons 425 and 426 to the right against the action of the spring 429. With the fourth speed shift valve piston 376 being in its upshifted position, line pressure is supplied from the port 369 to the ports 368 through the groove 378, and line pressure exists in the conduit 386 and port 422 of the 5-4 shift valve 90. When the 5-4 shift valve piston 426 is moved to the limit of its movement to the right, it uncovers the port 422, and line pressure iows through the groove 428, port 421, conduit 430 and port 417 to the left end of the 5-4 shift valve piston 426, and this line pressure from the port 417 in itself holds the piston 426 to the limit of its movement to the right, exclusive of the action of the plug 425.

The transmission is capable of driving the vehicle at a still higher speed in iifth speed drive than in fourth speed drive, and at this higher speed, the output pressure of the pump 76 is sufficiently high to move the inhibitor valve piston 249 to the limit of its movement to the right against the action of the spring 251 so as to connect the port 246, along with the ports 242, 243, 244 and 245,

With the line pressure supply port 241. Line pressure supplied to the port 246 flows through the conduit 261 to the fifth speed valve 89, and particularly its port 405. With the piston 409 being at the limit of its movement to the right, line pressure ows through the groove 411, the port 404, the conduit 413 and the port 398 and is applied to the left end of the plug 408. 1f the conduit 153 is subsequently taken out of communication with line pressure, as by movement of the selector valve piston 137, the fifth speed valve piston 409 nevertheless remains in its upshifted or fifth speed position. This line pressure derived from the downshift inhibitor valve port 246 is similar in its action to that derived from the other ports 242, 243, 244 and 245, in connection with the other shift valves, as will be noted.

Once the governor valve piston 319 has moved into its fifth speed position, line pressure is supplied to the port 317 from the port 314 through the valve groove 320, and this acts on the piston 339 which functions like the pistons 337 and 333 previously mentioned.

Assuming that the speed of the vehicle has dropped sufliciently, the downshift inhibitor valve piston 249 Will move into its fourth speed position connecting the ports 241, 242, 243, 244 and 245 but draining the port 246. The port 246 being connected by the conduit 261 with the port 405 of the fifth speed valve 39, will drain the left end of the cylindrical cavity 407 of the valve 89 through the port 393, the conduit 413, the port 404 and the groove 411 so that the fifth speed valve piston 409 may thereafter move to the left. If the selector valve piston 137 is then moved back into its D4 position,

23 the conduit 153 will be drained tothe sump, relieving the pressure eftectiveron the left end of the valve piston Y409 of the fifth speed Yvalve 89, and the piston 409 moves under the action of its spring 412 back into its fourth speed porsitioniblockingk the line pressure supply port 402. The` clutch piston 60 for the clutch 34 is then drained through the conduit 3782, the port 365, the groove 377, a-port 366, theconduit 384, the port 401, the groove 410, the port 400,V the conduit, 414, Ythe port418, the groove 427 and the relativelvopen port 420 in parallel with the restricted port 419 in the position of the -4 shift valve piston426 at the limit of its movement to the right. Due to the eiect of the line pressure transmitted through the conduit 430 and port 417 to the left end of the 5-4.shift valve piston 426, the piston 426 remains at the Vlimit'of,itsrnovement to the right, even though the pressure in the conduit 383 which ywas initially used for movingAthe'piston 426 to .the right, is drained through the lowerport 366 in communication with the conduitssq. Y

The disapply cavity 266b of the servomotor 262B for'therbrake 31 is also drained for this ratio change, the uid in draining ilowing through the conduit 385, aroundthe ball 391.0f the jet valve 388, the branch conduit 390 and the conduit 384 to the sump as mentioned in connection with the clutch 34. -The jet valve 388 functions to allow .arelatively wide open drain of the servomotor 262B, although the jet 389 is eiective Y for illing thedisapply cavity 26617 of the servomotor 262B in originally changing from fourth to fth speed drive. VThus the brake 31 is engaged, and the clutch 34 is disengaged, and the transmission is -again in fourth speed drive. Due to the function of the 5-4 shift valve 90, the draining of the clutch 34 and the disapply cavity 2,66b for the brake 31k are both relatively wide open and unrestricted.

As'has been previously described, the vpush start valve piston 229 is at the limit of its downward movement yagainst the action of thespring 231 whenever there is line pressure existing in the conduits 103 and 233. When, however, the engine of the vehicle is inoperative and no such pressure exists, then the piston 229A is at the limit ofY its movement upwardly due to the action of the. spring 231, and with the piston 229 Vin this position, uid under pressure may be derived from the driven shaft pump 76 for engaging the various clutchesY Yand brakes vof the transmission, so that the vehicle engine can be started by pushing or towing the vehicle. ln this case, the groove 230 of the push start piston 229 connectsV the ports 225 and 226, and uid pressure from the conduit 220 is supplied to the conduit 204 `and connected conduits. The selector valve piston 1-37 may be put into any of its forward drive positions for the purpose of starting the vehicle engine by pushing or towing the vehicle.

j The reverse drive through the transmission may Vbe completed by moving .the selector valve piston 137 into` its R position. In this position the piston 137 connects the ports 129 and 130 by means of the groove 138, andV line pressure is thus applied to the conduits 126, 294 and 166. The line pressure in conduit 126 tlows through the port 120 of the plug 119 in the pressure regulating valve 82, and the pressure acts on the upper end of the piston 123, so that the stem 124 of this piston is eiective on the'valve piston'115. The piston 123 thus augments the force due to the spring 125 on the regulator piston 115 and prevents the piston 115 from moving `upwardly so las Yto decrease the pressure from the pump 75 until a higher pressure exists in the conduit 103 with which the piston 115 is incommunication. The net eEect of the piston 123 on the piston 115 is to cause thepressure regulating valve 82 toV cooperate with the pump 75'in such a manner as to cause the pump to provide a higher regulated line pressure in Ythe Aconduit` 103 -for the reverse -drive as compared to the forwardV Y 24 drive.

Y Since this higher line pressure exists for reverse drive, it Yis desirable to reduceA the effectiveY cross section of the4 connection `between the pump '75 and the fluid coupling 26, and this is the function of the coupling valve 83. The increasedline pressure in the conduit `166 for reverse` drive is effectiveA on the upper end of the valve piston V161 to 'move the piston 161 against the action of its spring 163 into contact with the plug 164, and in this position the piston 161 blocks the lrestriction 156 but allows the restriction 155 to remain in communication ,with the -conduit 104 and port 158 suppliedwith linepressu're from the pump 75. VThe flow of fluidthrough the fluid coupling 26 for lreverse drive is thus kept approximately the same as for the forward drives.

A similar reduction VinV eiective size of the conduitsY connecting the pump with the lubricationconduit 193V is desirable for reverse drive due to the higher line pressure.v The line pressure in the conduit 126 is effective Athrough the conduit 195 and the port 186 on the right end of the piston 189 of the lubrication valve 91. Line pressure is supplied, as in the forward drives, from the conduit 103 through the conduits l194 and port 184 to the left end of the piston 189. Since line pressure exists onY bothends of the piston 189, the spring 191 is effective Vtohold the piston 189 at the limit of its movement to the left against the stop 192. The higher line pressure utilized for reverse drive supplied to ythe port 184 is effective on the' right end of the piston 188 to move the piston 188 to the limit of its movement to the left against the action of the spring 190 so as to open the port 182 with respect to the port 184. The ftwo ports 182 and 183 thus supply iiuid to the lubrication conduit 193, and since the port 182 is smaller than Vthe port 185` utilized for the forward drives, the approximate quantity of uid supplied to the conduit 193 for lubrication purposes remains the same for reverse drive as for the forward drives.

Y The line pressure in the conduit 294 is supplied through the port 285 to the left end of the reverse interlock valve piston 291 and moves the piston 291 to the limit of its movement to the right against the action of the spring 293 so as to connect the ports 288 and 287 by means of the groove 292 inA the piston 291. The port 288 is connected by means of the conduit 283 with the line pressure supply port 198 of the modulator valve 81, and fthe line pressure supplied through the port 288 flows throughv the groove 292, -port 287, conduit 296, port 364 of the fourth speed valve 88, groove 377, port 365 and conduit 382 to the piston 60 ofthe Vclutch 34. The clutch 34 is thus engaged, and since the torque carriedrin reverse drive by the clutch 34 is higher than fortheforward drives in which the clutch 34 is used, the clutch is engaged with the greater intensity due to the higher line pressure which isH suicient so that the clutch does not slip. The brake apply cavity 266a in the servomotor 262 for the brake 30vis connected by means of the conduit 263 with the line pressure supply Vport 198 of Ithe modulator valve 81 as for first and second speed forward drives previously described, and the brake 30 is eiective with the freewhecl brake 29 to complete the drive through the iirst planetary gear set 27. Y

As has just been described, the Huid pressure eective for engaging theiclutch34 for the reverse drive is supplied through the reverse interlock valve 84. The primary purpose of the reverse interlock valve 84 is to prevent the application of the clutch 34 for completing the reverse drive when there is any substantial forward-movement of the vehicle. Any substantial forward movement of the yvehicle causes the downshift inhibitor valve piston 249 to be moved to the right against the action of its spring 251 so that its groove 250 connects the line pressure port 241'with:the port 242. Y The port 242 is rconnected through y The. pressure for reverse drive may be V p.s.i., for example. Y 

